Generator assemblies, integrated drive generators, and methods of making generator assemblies

ABSTRACT

A generator assembly includes a rotor carrying a magnetic element, a bearing assembly supporting the rotor for rotation about a rotation axis, a bearing support structure extending circumferentially about the bearing assembly and configured for fixation to a housing, and a sleeve member. The sleeve member is arranged radially between the bearing assembly and the bearing support structure to limit a clearance defined radially between the bearing assembly and the bearing support structure. Integrated drive generators and methods of making generator assemblies are also described.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a division of U.S. application Ser. No. 16/694,548,filed Nov. 25, 2019, the disclosure of which is incorporated byreference herein in its entirety.

BACKGROUND

The present disclosure is generally related to rotating machines, andmore particularly to supporting rotors in in rotating machines likeelectrical generators.

Rotating machines, such as generators in aircraft electrical systems,commonly include a rotor. The rotor is generally supported for rotationrelative to a stator by a bearing. The bearing restrains movement of therotor to rotation about a rotation axis, typically by providing asliding in interface between a rotating bearing portion fixed relativeto the rotor and a stationary bearing portion fixed relative to thestator portion. In some rotating machines a clearance is providedbetween the stationary bearing portion and the housing to facilitateassembly of rotating machine. Such clearances can allow the bearing tobecome misaligned during service, increase loading on the bearing inrotating machines having eccentrically rotating loads, and/or increasedynamic loading of the bearing by reducing frequency spacing between thebearing natural frequency and the rotational speed of the rotatingmachine.

Such systems and methods have generally been acceptable for theirintended purpose. However, there remains a need in the art for improvedgenerator assemblies, integrated drive generators, and methods of makinggenerator assemblies and integrated drive generators having generatorassemblies.

BRIEF DESCRIPTION

A generator assembly is provided. The generator assembly includes arotor carrying a magnetic element, a bearing assembly supporting therotor for rotation about a rotation axis, a bearing support structureextending circumferentially about the bearing assembly and configuredfor fixation to a housing, and a sleeve member. The sleeve member isarranged radially between the bearing assembly and the bearing supportstructure to limit a clearance defined radially between the bearingassembly and the bearing support structure.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the bearing assembly is a radial bearing assembly.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the bearing assembly is a Conrad-type bearing assembly.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the bearing assembly is a first bearing assembly and that thegenerator assembly includes second bearing assembly supporting the rotorfor rotation about the rotation axis.

In addition to one or more of the features described above, or as analternative, further embodiments may include that the second bearingassembly is a straight bearing assembly.

In addition to one or more of the features described above, or as analternative, further embodiments may include that the first bearingassembly is a radial bearing assembly or a Conrad-type bearing assembly.

In addition to one or more of the features described above, or as analternative, further embodiments may include that the sleeve member hasan annular body defining a wedge-shaped profile.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the sleeve member has an inner end and an axially opposite outerend, the wedge-shaped profile tapering between the inner end and theouter end of the wedge-shaped profile.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the annular body defines an axial slot extending axially throughthe annular body, the axial slot spanning the wedge-shaped profile.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the bearing assembly has a bearing assembly axial width, the sleevemember has a sleeve member axial width, and that the sleeve member axialwidth is smaller than the bearing assembly axial width.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the bearing assembly includes an outer race defining a chamferedface, the chamfered faced extending circumferentially about the outerrace and seating thereon the sleeve member.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the chamfered face is arranged on an outboard end of the bearingassembly.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may includethat the outer race is an unbroken outer race and the bearing assemblyincludes an inner race extending circumferentially about the rotationaxis and two or more spherical elements distributed circumferentiallyabout the rotation axis between the inner race and the outer race of thebearing assembly.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may include aclamp arranged axially between the magnetic element and bearing supportstructure, the clamp fixed relative to the bearing support structure.

In addition to one or more of the features described above, or as analternative, further embodiments of the generator assembly may include ahousing with an interior enclosing the rotor, the bearing supportstructure arranged within the housing and fixing the bearing assembly tothe housing.

An integrated drive generator is also provided. The integrated drivegenerator includes a generator assembly as described above and aconstant speed drive. The constant speed drive is operably connected tothe rotor of the generator assembly.

In addition to one or more of the features described above, or as analternative, further embodiments of the integrated drive generator mayinclude that the bearing assembly is a radial bearing assembly or aConrad-type bearing assembly, the generator assembly further including astraight bearing assembly supporting the rotor for rotation about therotation axis and arranged on a side of the magnetic element oppositethe radial bearing assembly or the Conrad-type bearing assembly.

In addition to one or more of the features described above, or as analternative, further embodiments of the integrated drive generator mayinclude that the sleeve member has an annular body defining awedge-shaped profile; the bearing assembly includes an outer racedefining a chamfered face, the chamfered faced extendingcircumferentially about the outer race and seating thereon the sleevemember; and that the bearing assembly has a bearing assembly axialwidth, the sleeve member has a sleeve member axial width, and that thesleeve member axial width is smaller than the bearing assembly axialwidth.

A method of making a generator assembly is also provided. The methodincludes fixing a bearing support structure to a housing; arranging asleeve member within the bearing support structure; and seating abearing assembly within the bearing support structure, the bearingassembly supporting a rotor carrying a magnetic element for rotationabout a rotation axis, and the bearing assembly and the bearing supportstructure defining therebetween a radial clearance. The sleeve member istranslated axially along the rotation axis relative to bearing assemblyto limit a clearance defined radially between the bearing assembly andthe bearing support structure.

In addition to one or more of the features described above, or as analternative, further embodiments of the method may include closing theclearance between the bearing assembly and the bearing supportstructure.

Technical effects of the present disclosure include the capability toclose a clearance between a bearing assembly and a bearing supportstructure subsequent to assembly of the bearing assembly and supportassembly within a generator. In certain examples the bearing supportstructure, bearing assembly, and rotor carrying a magnetic element areassembled within a housing with a clearance defined between the bearingsupport structure and the bearing assembly, and the clearance thereafterclosed by driving the sleeve member axially to a position radiallybetween the bearing assembly and the bearing support structure. Inaccordance with one or more examples closing the clearance reduces (oreliminates entirely) bearing misalignment, increases stiffness and/ornatural frequency of the bearing, and limit amplification of loading onthe bearing assembly due to eccentric rotation of the rotor.

BRIEF DESCRIPTION OF THE DRAWINGS

The following descriptions should not be considered limiting in any way.With reference to the accompanying drawings, like elements are numberedalike:

FIG. 1 is a schematic cross-sectional view of an aircraft carrying agenerator assembly constructed in accordance with the presentdisclosure, showing an integrated drive generator having a generatorassembly;

FIG. 2 is a schematic exploded view of the generator assembly of FIG. 1according to an example, showing sleeve member and a clamp/bearingsupport structure assembly seating a first bearing assembly supporting arotor of the generator assembly;

FIG. 3 is a cross-sectional side view of a portion of the generatorassembly of FIG. 1 according to the example, showing first bearingassembly captive within the clamp/bearing support structure assemblywith the sleeve member;

FIGS. 4-6 are perspective, end and cross-sectional views of the sleevemember of FIG. 3 , showing an axial slot and a wedge-shaped profiledefined by the sleeve member for closing a radial clearance definedbetween the clamp/bearing support structure assembly and the bearingassembly;

FIG. 7 is a schematic view of a sleeve member arranged radially betweenthe bearing assembly and the bearing support structure of the generatorassembly of FIG. 1 , showing the sleeve member translating relative tothe bearing assembly between the bearing assembly and the bearingsupport structure; and

FIG. 8 is a block diagram of a method of making a generator assembly,showing operations of the method according to an illustrative andnon-limiting example of the method.

DETAILED DESCRIPTION

Reference will now be made to the drawings wherein like referencenumerals identify similar structural features or aspects of the subjectdisclosure. For purposes of explanation and illustration, and notlimitation, a partial view of an example of a generator assemblyconstructed in accordance with the disclosure is shown in FIG. 1 and isdesignated generally by reference character 100. Other embodiments ofgenerator assemblies, integrated drive generators, and methods of makinggenerator assemblies in accordance with the present disclosure, oraspects thereof, are provided in FIGS. 2-8 , as will be described. Thesystems and methods described herein can be used to limit (or closeentirely) clearances between bearing assemblies and bearing supportstructures in rotating machines, such as in integrated drive generatorsfor aircraft electrical systems, though the present disclosure is notlimited to integrated drive generators or to generators assemblies ingeneral.

Referring to FIG. 1 , a vehicle 10, e.g., an aircraft, is shown. Thevehicle 10 includes an electrical system 12, a gas turbine engine 14,and a generator assembly 100. The electrical system 12 includes thegenerator assembly 100, an electrical load 16, and a power bus 18. Theelectrical load 16 is connected to the generator assembly 100 by thepower bus 18. The generator assembly 100 is operably associated with thegas turbine engine 14 and is configured to generate electrical power 20using mechanical rotation 22 (shown in FIG. 2 ) communicated thereto bythe gas turbine engine 14. In certain examples the generator assembly100 is operably associated with the gas turbine engine 14 through anaccessory gearbox 24 to receive therethrough the mechanical rotation 22.In accordance with certain examples the generator assembly 100 isoperably associated with the gas turbine engine 14 through a constantspeed drive 202 as an integrated drive generator 200. Although shown anddescribed herein in generator assembly for an aircraft it is to beunderstood and appreciated that other types of generators can benefitfrom the present disclosure.

With reference to FIG. 2 , the generator assembly 100 is shown. Thegenerator assembly 100 includes a housing 102, a stator winding 104, anda rotor 106. The generator assembly 100 also includes a magnetic element108, a first bearing assembly 110, and a second bearing assembly 112.

The housing 102 has an interior 114. The stator winding 104, the rotor106, and magnetic element 108 are arranged within the interior 114 ofthe housing 102. The magnetic element 108, the first bearing assembly110 and the second bearing assembly 112 are also arranged within theinterior 114 of the housing 102.

The stator winding 104 is electrically connected to the power bus 18(shown in FIG. 1 ) and is arranged with provide a flow of electriccurrent. In this respect the stator winding 104 is electromagneticallycoupled to the magnetic element 108 such that rotation of magneticelement 108 relative to the stator winding 104 induces a flow ofelectric current in the stator winding 104. In certain examples the flowof electric current is an alternating current (AC) flow.

The magnetic element 108 is fixed relative to the rotor 106. In certainexamples the magnetic element 108 includes a permanent magnet 116. Inaccordance with certain examples the magnetic element 108 includes awinding 118. It is also contemplated that the magnetic element 108 caninclude both the permanent magnet 116 and the winding 118.

The rotor 106 is supported for rotation about a rotation axis 120 withinthe interior 114 of the housing 102 by the first bearing assembly 110and the second bearing assembly 112. In certain examples the firstbearing assembly 110 is a radial bearing assembly, e.g., a ball bearingassembly. In accordance with certain examples the second bearingassembly 112 is a straight bearing assembly. Straight bearing assembliesallow the rotor 106 to slide axially in response to heating of thegenerator assembly 100 during operation, such as due to differentialbetween elongation of the rotor 106 and the housing 102 duringoperation. Although shown and described herein as having a radialbearing assembly and a straight bearing assembly, it is to be understoodand appreciated that rotating machines having other types of bearingassemblies can also benefit from the present disclosure.

With reference to FIG. 3 , a portion of the generator assembly 100 isshown including the first bearing assembly 110. The first bearingassembly 110 includes an inner race 122, an outer race 124, and aplurality of spherical elements 126. The inner race 122 is fixed inrotation relative to the rotor 106 for rotation with the rotor 106 aboutthe rotation axis 120. The plurality of spherical elements 126 aredistributed circumferentially about the inner race 122 and the rotationaxis 120. The outer race 124 extends circumferentially about the innerrace 122 and the plurality of spherical elements 126, and is configuredfor fixation relative to the housing 102. Fixation of the first bearingassembly 110 to the housing 102 is accomplished by a clamp 128, abearing support structure 130, and a retainer 132. In certain examplesthe outer race 124 can be an unbroken race, limiting load on the firstbearing assembly 110 and thereby extending the expected service life ofthe first bearing assembly 110.

The bearing support structure 130 is fixed within the interior 114 ofthe housing 102 and has a bearing seat 134. The bearing seat 134radially bounds the first bearing assembly 110, extends thereabout, andseats thereon the first bearing assembly 110. A plurality of firstfasteners 136 (shown in FIG. 2 ) extend through the bearing supportstructure 130 and threadably fixes the bearing support structure 130 tothe housing 102 and about the rotation axis 120.

The clamp 128 is arranged within the interior 114 of the housing 102 andhas a bearing support structure seat 138. The bearing support structureseat 138 radially bounds the bearing support structure 130, extendsabout the bearing support structure 130, and seats thereon the bearingsupport structure 130. A plurality of second fasteners 140 extend thoughthe retainer 132 and the housing 102 to threadably fix the clamp 128against the bearing support structure 130 with the first bearingassembly 110 captive between the clamp 128 and the bearing supportstructure 130. A radial clearance 142 is defined between the outer race124 and of the first bearing assembly 110 and the bearing supportstructure 130.

As will be appreciated by those of skill in the art in view of thepresented disclosure, the clearance 142 facilitates assembly of thegenerator assembly 100 by allowing the bearing support structure 130 tobe fixed with the interior 114 of the housing 102 and receive thereonthe rotor 106 and the first bearing assembly 110 with the clamp 128mounted thereon. As will also be appreciated by those of skill in theart in view of the present disclosure, such clearances can, in somegenerator assemblies, limit reliability of the generator assembly. Forexample, clearances can allow the bearing assembly to become misalignedrelative to the rotation axis, increasing the load exerted on thebearing assembly. Clearances can also reduce the stiffness provided bythe bearing assembly, limiting the frequency spacing between the bearingassembly and the nominal speed of rotor such that dynamic loading of thebearing assembly, potentially reducing service life of the bearingassembly. And in some generators such clearances can allow the outerrace to orbit relative to the generator stator—the orbiting in turncausing fretting wear occurring and/or generating debris, posing aforeign object damage hazard. To limit misalignment, increase stiffness,and/or present orbiting the generator assembly 100 includes the sleevemember 144.

The sleeve member 144 is arranged radially between the first bearingassembly 110 the bearing support structure 130. More specifically, thesleeve member 144 is arranged between the outer race 124 of the firstbearing assembly 110 and the bearing seat 134 of the bearing supportstructure 130 to limit (or close entirely) the radial clearance 142.Limiting (or closing entirely) the radial clearance 142 fixes the outerrace 124 of the first bearing assembly 110 relative to the bearingsupport structure 130, reducing (or eliminating entirely) misalignmentof the first bearing assembly 110 relative to the rotation axis 120,stiffening the first bearing assembly 110, and/or preventing orbiting ofthe outer race 124 relative to the bearing support structure 130. It iscontemplated that the radial clearance 142 be limited (or closedentirely) subsequent to the assembly of the rotor 106 (carrying thefirst bearing assembly 110 and the clamp 128 thereon), the radialclearance 142 thereby facilitating assembly of the generator assembly100 prior to being limited (or closed entirely).

With reference to FIGS. 4-6 , the sleeve member 144 is shown. As shownin FIG. 4 , the sleeve member 144 includes an annular body 146 having aninboard edge 148, an outboard edge 150, and a defines a slot 152extending between the inboard edge 148 and the outboard edge 150. Theoutboard edge 150 is arranged to abut the bearing support structure 130(shown in FIG. 2 ) within the interior 114 (shown in FIG. 2 ) of thehousing 102 (shown in FIG. 2 ) when the sleeve member 144 is installedwithin the generator assembly 100 (shown in FIG. 1 ). The inboard edge148 is arranged to oppose the clamp 128 (shown in FIG. 2 ) within theinterior 114 of the housing 102 when the sleeve member 144 is installedwithin the generator assembly 100 such that the clamp 128 is arrangedaxially between the sleeve member 144 and the magnetic element 108(shown in FIG. 2 ). It is contemplated that the slot 152 extendsubstantially in parallel with the rotation axis 120 (shown in FIG. 2 )and between the bearing support structure 130 and the clamp 128.

As shown in FIG. 5 , the annular body 146 extends circumferentiallyabout the rotation axis 120 (shown in FIG. 2 ) such that the outboardedge 150 is radially offset from the rotation axis 120. In certainexamples the sleeve member 144 is clocked about the rotation axis 120such that slot 152 is positioned above the rotation axis 120 relative togravity. In accordance with certain examples the sleeve member 144 canbe seated within the interior 114 of the housing 102 such that the slotreceives a pin 154, fixed relative to the housing 102, to fix positionof the sleeve member 144 about the rotation axis 120 during assembly ofthe generator assembly 100 (shown in FIG. 1 ).

As shown in FIG. 6 , the sleeve member 144 has a wedge-shaped profile156. The wedge-shaped profile 156 extends axially between the inboardedge 148 and the outboard edge 150. It is contemplated that thewedge-shaped profile 156 taper between the inboard edge 148 and theoutboard edge 150, the inboard edge 148 having a smaller surface areathan the surface area of the outboard edge 150. In certain examples thesleeve member 144 is formed from a metallic material 158. In accordancewith certain examples the metallic material 158 has a coefficient ofthermal expansion that corresponds to the coefficient of thermalexpansion of the first bearing assembly 110, the bearing supportstructure 130, and/or the clamp 128 such that clearance remains limited(or closed) during heating and cooling of the generator assembly 100during operation.

With continuing reference to FIGS. 3 and 7 , the sleeve member 144 seatsradially between the first bearing assembly 110 and the bearing supportstructure 130. More specifically, the sleeve member 144 is radiallyinterposed between the outer race 124 of the first bearing assembly 110and the bearing support structure 130. In certain examples the outerrace 124 has radially-outer chamfer 160. In certain examples the sleevemember 144 has a sleeve member axial width 162 that is smaller than abearing member axial width 164. In accordance with certain examples theradially-outer chamfer 160 is defined on an axially outer edge 166 ofthe outer race 124 such that a radially outer face 168 (shown in FIG. 4) of the sleeve member 144 is substantially parallel to the rotationaxis 120.

As shown in FIG. 7 , the radially-outer chamfer 160 cooperates with thewedge-shaped profile 156 such that, as the sleeve member 144 translatesaxially along the rotation axis 120 during assembly, the radialclearance 142 decreases in radial width (or closes entirely) such thatthe outer race 124 of the first bearing assembly 110 is fixed inrotation relative to the bearing support structure 130. In this respect,as shown at reference I, seating the first bearing assembly 110 withinthe bearing support structure 130 causes the first bearing assembly 110and the bearing support structure 130 to define a first gap width Abetween one another. As shown at reference II, translating the sleevemember 144 along the rotation axis 120 relative to the first bearingassembly 110 causes the first bearing assembly 110 and the bearingsupport structure 130 to define between a second gap width B between oneanother, the second gap width B larger than the first gap widthA—limiting the radial clearance 142 between the first bearing assembly110 and the bearing support structure 130. In certain examples theradial clearance 142 is closed by translating the sleeve member 144along the rotation axis 120 such that the first bearing assembly 110 andthe bearing support structure 130 define a third gap width between oneanother, the third gap width C larger than the second gap width B.

With reference to FIG. 8 , a method 300 of making a generator assembly,e.g., the generator assembly 100 (shown in FIG. 1 ), is shown. As shownwith box 310, the method 300 includes fixing a bearing support structurewithin the interior of a housing for a generator assembly, e.g., thebearing support structure 130 (shown in FIG. 2 ) within the interior 114(shown in FIG. 2 ) of the housing 102 (shown in FIG. 2 ). Fixation canbe accomplished by fastening the bearing support structure within theinterior of the housing, e.g., with the plurality of first fasteners 136(shown in FIG. 2 ).

As shown with box 320, the method 300 also includes supporting a rotorcarrying a magnetic element about a rotation axis within the housing,e.g., the rotor 106 (shown in FIG. 2 ) carrying the magnetic element 108(shown in FIG. 2 ). A clamp, e.g., the clamp 128 (shown in FIG. 2 ), ispositioned about the rotor, as shown with box 222. An inner race ofbearing assembly, the inner race 122 (shown in FIG. 3 ) of the firstbearing assembly 110 (shown in FIG. 2 ), is fixed to the rotor such thatthe inner race is fixed in rotation relative to the rotor, as shown withbox 224. The rotor, including the clamp and the bearing assembly, ispositioned within the housing such that the bearing assembly is arrangedradially between the rotor and the bearing support structure with aclearance, e.g., the radial clearance 142 (shown in FIG. 3 ), is definedtherebetween, as shown with box 326.

As shown with box 330, a sleeve member, e.g., the sleeve member 144(shown in FIG. 3 ), is arranged radially between the bearing assemblyand the bearing support structure. The sleeve member 144 is translatedalong the rotation axis relative to the bearing assembly, as shown withbox 340. As the sleeve member translates along the rotation axisrelative to the bearing assembly the sleeve member limits the clearancedefined between the bearing assembly and the bearing support structure,as shown with box 350, e.g., by making a radial distance between thebearing assembly and the bearing support structure smaller. In certainexamples the clearance between the bearing assembly and the bearingsupport structure is closed, e.g., such that no radial distance isdefined between the bearing assembly and the bearing support structure,as shown by box 352. In accordance with certain examples closing theclearance by translating the sleeve member relative to the bearingassembly can create an interference fit between the sleeve member andeither (or both) the bearing assembly and bearing support structure.

Rotating machines commonly employ bearings to support rotary componentsfor rotation relative to stationary components. In some rotatingmachines there can be clearance between the bearing and the stationaryportion of the rotating machine, the clearance enabling assembly of therotating machine. While generally acceptable for its intended purposeclearance between the bearing and stationary components of the rotatingmachine increase eccentric loading of the bearing, potentially reducingthe expect service life of the bearing. Clearance between the bearingand stationary components of the rotating machine can also result inmisalignment of the bearing, also potentially limiting the expectedservice life of the bearing. And clearance between the bearing and thestationary components can also reduce bearing life due to misalignmentand/or stiffness variation in intermediate structures supporting thebearing relative to other stationary structures.

In examples described herein a portion of clearance between the bearingand the stationary structure of a rotating machine, e.g., a generator,is closed subsequent to assembly of the rotor within the stator of therotating machine. In certain examples sleeve is arranged between thebearing and the stator of the rotating machine. The sleeve can be closedunder outside and opened under inside pressure such that the sleevediameter can be changed, i.e., be made smaller or larger, depending uponthe pressure applied to the sleeve. In accordance with certain examples,when the sleeve is installed between the bearing and stationarystructure such as a bearing support the sleeve diameter will self-adjustto the inner diameter of the bearing support. Self-adjustment can beaccomplished, for example, by clamping the sleeve between the stationarystructure and a retaining plate. It also contemplated that, inaccordance with certain examples, that the material forming the sleevebe selected such that thermal expansion of the sleeve corresponds, e.g.,matches, that of thermal expansion of the bearing.

Technical effects of the present disclosure can include limiting (orpreventing entirely) distortion of the outer race of the bearing.Technical effects also include delaying (or preventing entirely) thetendency of the bearing to orbit within, and frictionally against, theseat defined by the stationary structure—limiting (or preventingentirely) the generation of debris from the orbiting which can otherwisepresent a foreign object damage hazard to the rotating machine.Technical effects additionally the employment of bearings havingunbroken (non-broken) outer races.

The term “about” is intended to include the degree of error associatedwith measurement of the particular quantity based upon the equipmentavailable at the time of filing the application.

The terminology used herein is for the purpose of describing particularembodiments only and is not intended to be limiting of the presentdisclosure. As used herein, the singular forms “a”, “an” and “the” areintended to include the plural forms as well, unless the context clearlyindicates otherwise. It will be further understood that the terms“comprises” and/or “comprising,” when used in this specification,specify the presence of stated features, integers, steps, operations,elements, and/or components, but do not preclude the presence oraddition of one or more other features, integers, steps, operations,element components, and/or groups thereof.

While the present disclosure has been described with reference to anexemplary embodiment or embodiments, it will be understood by thoseskilled in the art that various changes may be made and equivalents maybe substituted for elements thereof without departing from the scope ofthe present disclosure. In addition, many modifications may be made toadapt a particular situation or material to the teachings of the presentdisclosure without departing from the essential scope thereof.Therefore, it is intended that the present disclosure not be limited tothe particular embodiment disclosed as the best mode contemplated forcarrying out this present disclosure, but that the present disclosurewill include all embodiments falling within the scope of the claims.

What is claimed is:
 1. A method of making a generator assembly,comprising: fixing a bearing support structure to a housing; arranging asleeve member within the bearing support structure, wherein the sleevemember has a wedge-shaped profile with a flat inner surface and a slopedouter surface; wherein the sleeve member has an inner end and an axiallyopposite outer end, wherein the wedge-shaped profile tapers between theinner end and the outer end of the wedge-shaped profile; seating abearing assembly within the bearing support structure, the bearingassembly supporting a rotor carrying a magnetic element for rotationabout a rotation axis, the bearing assembly and the bearing supportstructure defining therebetween a radial clearance; and translating thesleeve member axially along the rotation axis relative to bearingassembly to limit a clearance defined radially between the bearingassembly and the bearing support structure.
 2. The method of claim 1,wherein limiting the clearance includes closing the clearance betweenthe bearing assembly and the bearing support structure.
 3. The method ofclaim 1, wherein the bearing assembly is a radial bearing assembly. 4.The method of claim 1, wherein the bearing assembly is a Conrad-typebearing assembly.
 5. The method of claim 1, wherein the bearing assemblyis a Conrad-type bearing assembly.
 6. The method of claim 1, wherein thebearing assembly is a first bearing assembly; and the method furthercomprising includes seating a second bearing within the bearing supportstructure such that it also supports the rotor for rotation about therotation axis.
 7. The method of claim 6, wherein the second bearingassembly is a Conrad-type bearing assembly.
 8. The method of claim 6,wherein the first bearing assembly is a radial bearing assembly or aConrad-type bearing assembly.
 9. The method of claim 1, wherein theannular body defines an axial slot extending axially through the annularbody, the axial slot spanning the wedge-shaped profile.
 10. The methodof claim 1, wherein the bearing assembly has a bearing assembly axialwidth, wherein the sleeve member has a sleeve member axial width, andwherein the sleeve member axial width is smaller than the bearingassembly axial width.
 11. The method of claim 1, wherein the bearingassembly comprises an outer race defining a chamfered face, thechamfered faced extending circumferentially about the outer race andseating thereon the sleeve member.
 12. The method of claim 11, whereinthe chamfered face is arranged on an outboard end of the bearingassembly.
 13. The method of claim 11, wherein the outer race is anunbroken outer race, the bearing assembly further comprising: an innerrace extending circumferentially about the rotation axis; and aplurality of spherical elements distributed circumferentially about therotation axis and between the inner race and the outer race of thebearing assembly.
 14. The method of claim 1, further comprising:arranging a clamp axially between the magnetic element and bearingsupport structure, the clamp fixed relative to the bearing supportstructure.